Control for machine tools



June 6, 1939. f M. L. TRAWN 2,160,920

CONTROL FOR MACHINE TooLs Filed July 3, 1936 2 Sheets-Sheet 2 www@ Patented June 6, 1939 PATENT oFFlcE CONTROL FOR MACHINE TOOLS Marion L. Strawn, Rockford, Ill., assigner to The Ingersoll Milling Machine Company, Rockford, Ill.. a corporation of Illinois yApplication July 3, 1936, Serial No. 88,726

10 Claims.

This invention relates generally to automatic machine lcools and more particularly to a. mech-v of the control mechanismfail to function properly.

A more detailed object is to provide a novel ll mechanism for controlling the cyclic movements of a machine tool element having two power driven devices and means for combining the motions thereof to produce rapid approach move- -ment of the element when both of said devices ,20 are energized, to produce-rapid return motion when both of said devices are deenergized, and to effect other control of the machine tool element when one or the other of said devices is energized.

The invention also resides in the novel char- 25 acter -of the mechanism for combining the motions of the power actuated device and applying the same to the member by which the cyclic movements ofthe machine tool element are controlled.

Further objects and advantages of the inveng', tion will become apparent as the following description proceeds and the features of novelty which characterize the invention are pointed out with particularity in the claims annexed to and forming a part of this specification.

35 For a better understanding of the invention reference may be had to the accompanying drawings, in which Figure 1 is a side elevation of a portion of a machine tool embodying the invention.

Fig. 2 is an enlarged detail View partly in section of a portion of the control mechanism for the machine tool shown in Fig. 1.

Fig. 3 is a fragmentary plan view of a portion of the control mechanism shown in Fig. 2 being.

partly in section along the line 3-3.

Fig. 4 is a wiring diagram of the electric control mechanismV of the machine tool shown in Fig. 1.

Fig. 5 is a detail view partly in section of the 50 fluid actuating mechanism for the machine tool shown in Fig. 1 and its associated iluivd control mechanism, the latter being shown in its neutral position.

Figs. 6, 7 and 8 are similar to Fig'. 5 but illusu trate the fluid cdntrol mechanism in its rapid (Cl. S30-21.5)

approach, feed and rapid return positions, respectively.

Fig. 9 illustrates a modified form of control arrangement embodying the invention, this modiedvcontrol arrangement being of the uid oper- 5 ated type as contrasted with the electrical control shown in Figs. I to 4 inclusive.

Referring more particularly to the drawings, the invention has been shown for purposes of illustration as applied to a milling machine. Thus,

las illustrated in Fig. l, this machine includes a bed or base I0 having a table Il slidably mounted thereon for endwise or translatory movement. A work piece I2 is mounted on the table Ii and is moved by the latter into engagement with the-l5 usual motor driven cutter I3.

Translatory movement of the table II is effected by a power actuating means, which is illustrated in the drawings in thel form of a hydraulic mechanism including a piston'. I4 slidably mounted .in a cylinder I5 and rigidly connected to a bracketv I6 on the lower side of the table Il by a piston rod I1. In general, pressure fluid is applied to selected portions of the mechanism and at a predetermined pressure to move the table II in a selected direction and at a predetermined speed. Thus, in the construction shown, pressure fluid is supplied through a conduit IB to the left face of the piston I4 as viewed in Fig. 1 to move the table II to the right, or pressure fluid may be supplied through a conduit I9 to the right face of the piston I4 to move the table Il to the left. Also, as shown in Fig. 5, for example, the pressure of the fluid passing through the conduit I8 may be reduced by a 35 throttle valve 20 so as to decreasev the volume supplied to the cylinder I5 and thereby establish l a selected feed rate. y

Referring particularly to Figs. 5 to 8 inclusive,

a multiple position valve is provided lor con- 40 trolling the flow of pressure fluid to the cylinder l5 and comprises a member 2I slidably mounted in a casing 22. Fluid under pressure is supplied to an inlet port 23 of the casing 22 from a motor operated pump 24 through a conduit 25. The 45 casing 22 is provided with three outlet ports 26, 21 and 28. The ports 2li and 21 communicate with the conduit I8 through branch conduits 29 and 29' respectively, the pressure reducing valve 20 being interposed in the latter. The port 28 communicates with the conduit` I9.

When the valve member 2l is in its neutral Aposition shown in Fig. 5, collars 30 and 3|` thereonclosethe outlet ports 26, 2l and 28'so that no pressure fluid is supplied to either end of the piston i4. The conduit 25 from the pump 24 communicates with a return conduit 32 through a pressure operated relief valve 33 so that the uid pumped thereby will be returned to a reservoir 34 through the valve 33 and conduit 32 when the pressure in the conduit 25 reaches a predetermined maximum value.

The valve member 2| is provided with an operating stem 35 by means of which it may be shifted to a plurality of selected positions to cause feed and rapid traverse motions of the machine tool element. When the valve member 2| is moved axially to the position shown in Fig. 6, the collar 30 thereon is moved out of registry with the ports 2B and 21 so that uid under pressure flows from the conduit 25 through the valve casing 2|, ports Y26 and 21, conduits 29 and 29a to the main condint I8, and then to the interior of the cylinder l5 on the right hand side of the piston I4. At the same time, however, the collar 3| prevents pressure fluid from passing from the conduit 25 to the conduit I 9. 'I'he high pressure uid thus applied to the left face of the piston I4 causes the same to be moved through the cylinder I5 and results in a rapid approach movement ofthe table II. Any fluid contained in the right hand portion of the cylinder I5 is discharged from the conduit I9 into the valve casing 2| and then through a passage 3G formed therein to the return conduit 32.

Movement of the valve member 2 I to the posi- Ition shown in Fig. 'I causes the collar 30 thereon to close the port 25 while leaving the port 21 open. Pressure fluid is thus supplied from the pump 24 through the conduit 25, valve casing 22, port 21, reducing valve 20, conduits 29a and I8 to the left hand portion of the cylinder I5. The valve 20 reduces the volume of the uid applied to the left hand face of the piston I 4 so that a slower feed movement of the table I I is had. It will be noted that the pressure reducing or throttle valve 20 is provided with an adjustable member 28 by means of which the reduction in volume of the uid passing therethrough may be selectively varied.

Rapid return movement of the table II is eiected by moving the valve member 2| to the position shown in Fig. 8. When in this position the collar 30 thereon eiectively prevents communication between the fluid supply conduit 25 and the ports 26 and 21. The collar 3| uncovers the port 28, however, so that fluid under pressure is supplied therethrough to the conduit I9 and thence to the right hand face of the piston I4. The application ofl pressure duid to the right hand face of the piston I 4 thus causes the table II to be moved to the left as viewed in Fig. l with a rapid return movement.

The invention contemplates actuation of the valve control member by a plurality of devices normally biased into one position and adapted to be moved in second positions by individual power actuators arranged to be energized in different combinations in a manner such as to provide for absolute safety in the operation of the machine tool. To this end, provision is made for movement of the valve member into rapid approach position by Aenergization of both of said actuators and preferably for movement to rapidv aisance the actuating mechanism is conditioned for rapid return movement in the event of complete failure of the actuators to operate.

In the form shown in Figs. 1 to 4, the valve control mechanism is electrically actuated, the actuators above referred to taking the form of solenoids 5I) and 5| having armatures 52 and 53 which constitute the movable devices and are connected through a differential mechanism to the valve stem 35. Herein, the diierential mechanism comprises an equalizing bar 38 pivotaily joined at its center 5I to the stem 35 and connected at opposite ends to links 36 and 31 which in turn are joined to the respective armatures 52 and 53. Each solenoid plunger is normally biased to a predetermined position by a pair of helical` compression springs 43 and 44 which surround rods 39 and 42 and bear at one of their ends against lateral projections 40 on the armatures. At the other ends, the springs are seated in cupshaped retainers 45 threaded into a supporting wall 46.

The rods 39 and 42 carry pistons 41 which are slidably mounted in cylinders 48 threaded on the outer ends of the cup-shaped retainers 45. Small apertures 49 are formed in the outer ends of the cylinders 48 so that the latter form dashpots for limiting the speed of actuation of the armatures 52 and 53 under the action of the solenoids.

It will be seen that when either of the solenoids 50 or 5| is energized, its corresponding armature 52 or 53 will be attracted, thus moving the attached end of the equalizing lever 38 outwardly and compressing the 'biasing spring of the attached operating member. At the same time, the dashpots formed by the cooperating cylinders 48 and pistons 41 limit the speed of movement of the armatures 52 and 53 to a safe value.

A suitable energizing circuit, best shown in Fig. 4, has been provided for the solenoids 50 and 5I in order to cause movement of the machine tool element in the desired automatic cycle. This control circuit is preferably interconnected with the supply circuits of the cutting tool and pump driving motors in order that they may be electrically interlocked. Upon reference to Fig. 4, it will be seen that current is supplied to a cutting tool drive motor 55 and to a pump drive motor 55 from main supply lines 56, 51 and 58 through branch conductors 59 and 50 respectively.

The connection of the branch conductors 59 to the main supply lines is controlled by a contactor biased toits open position and having an actuating winding 5| as well as main contact members 52. Similarly, the connection of the branch conductors 50 to the main supply lines is controlled bya contactor biased to its open position and having an energizing Winding 63 as well as main contacts 64.

Upon closure of a starting switch or push button 65, the energizing circuits of the contacter actuating windings 6| and 63 are completed. It Will be noted that the windings 6I and 55 are connected in parallel by conductors B6 and 61. The conductor 51 is permanently connected to the supply line 58 by a conductor 53. The conductor 66 is connected with the supply line 56 upon closure of the starting switch 65 through conductors |59 and l0, switch 55, conductor i i, normally closed stop push button 12 and conductors 13 and 14. Upon such energization of the contactor windings 6| and 83, the contactors are closed and' the driving motors 54 and 55 energized. The winding 6| also closes a sealing contact 15 therefor which shunts thc starting push button 65 through conductors 16 and 11 so that the windings 6I and 63 will remain energized upon release of the normally open starting push button 65.

Closure of the starting push button 65 as described labove also serves to energize the solenoid so that the controlv mechanism is movedto its neutral position.` Thus, upon reference to Fig. 4,

it will beseen that closure of the push button 65 completes a circuit from Vsupply line 56 through conductors 14, 13, normally closed stop push button 12, conductor 1|,.switch 65, conductors 10 and 18, while ythe other terminal of thesolenoid 5| is connected to the supply line 58 through conductors 19 and 88 and a limit switch 8|. The sealing circuit formed by the conductors 16 and 11 and contact 15 also serves to maintain thesolenoid 5| energized upon release of the starting button 65. v

When the solenoid 5| is thus energized, its armature 53 is attracted so that the springs 43 are, compressed and the operating member 31 movedl to the left into the position shown in Fig. 2. As a result, the pivotal connection 4I between the floating lever 38 and valve operating rod 35 is ymoved to the neutral position indicated in Figs.

2 and 5. It is particularly advantageous to have the control mechanism arranged in such a manner that the neutral position requires the energization of only one of the actuating members.

Otherwise, if it were necessary to actuate both.

of the machine tool is initiated by closing a normally open push button 82. This completes the energizing circuit for a normally open contactor 83 which in turn controls the energization of the solenoid 50. Thus, one terminal of an actuating 'winding 84 of the contactor 83 is connected to the conductor 18 through a conductor 85, push button 82, conductor 86 and normally closed stop push button 82a. As was pointed out above, the

conductor 18 is connected to the supply line 56 at all times after the starting push button 65 is closed until the machine is stopped. The other terminal of the contactor actuating winding 84 is connected to the supply line 58 through the conductor 68. The contactor 83 is provided with an auxiliary contact 81 which serves to complete a sealing circuit for the contactor so that it will remain closed after the release of the momentarily actuated push button 82. Thus, the contact 81- completes a shunt circuit about the push button 82 through a conductor 88 and limit switch 89. The closure of the contactor 83 also closes its main contacts 90 completing an energizing circuit for the solenoid 58. One terminal of the solenoid is permanently connected to the conductor 14 which is in turn connected to the supply line 56 while the other terminal of the solenoid 50 is connected to conductor 68 through a conductor 9| and contacts 90.

Energization of the solenoid 58 results in attraction of armature 52 and movement of the same to the left as viewed in Fig. 2. Since the so1enoid'5l is already energized at this point in the cycle, the pivot point 4| on the floating lever 38 is moved to the rapid approach position indicated in Figs. 2 and 6. In such position, the

ably secured to the sideof the table and is ladapted to actuate the limit switch 8| when it comes in contact therewith. The dog 92 is pivotally mounted and maybe positioned at any selectedlpoint along -the side of the table A stop pin 92a prevents clockwise movement of the dog 92 past the position shown but permits a free counter-clockwise movement thereof. The limit switch 8| is preferably of a snap acting'type and includes an over-center spring arrangement adapted to hold the same in either of the two positions to which it may be moved. Thus, when the dog 92 engages the limit switch 8| during the rapid approach movement ofthe table II, the switch 8| is snapped to its open position and remains in such open position until it is again actuated in the opposite direction.

Opening of the limit switch 8| disconnects the solenoid 5| from the supply line 58 releasing the armature 53 for outward movement by the compression springs 43. When the solenoid 5| is deenergzed while the solenoid 50 remains energized, the floating lever 38 is moved so that tlle pivot point 4| with the'valve stem 35 assumes the feed position indicated by the dot-dash line in Figs. 2 and 7. As a consequence, the volume of fluid supplied to the machine tool actuating mechanism is reduced as described above so that the translatory motion of the table is continued at a relatively slower'feed rate.

A further arrangement is provided for automatically reversing the direction of movement of the table I| upon the completion of the desired cutting operation and in addition, the table is moved in the reverse direction at a rapid return rate. The control mechanism is so arranged that all of its parts will be in their normal or deenergized positions when this rapid return movement takes place. This is an advantageous safety precaution as will be apparent from a brief analysis of the operation of the machine. Thus, if the electrical energy or other power supplied to the vmachine fails for any reason, the machine will fail safe". That is to say, in the present in- 5| will be deenergized, and the control mechanism will be shifted to its rapid return position. In this way, the momentum of the pump driving motor 55, coasting to a stop, is utilized to supply fluid under pressure for moving the work piece I2 away from the cutting tool I3 so that it is safely disengaged therefrom.

In the construction illustrated, the rapid return movement of the table is initiated by a dog 93 detachably secured to the side ofthe table I| at any desired point. At the completion of the selected-feed motion of the table Il, the dog 93 engages the limit switch 89 and moves the same momentarily to its open position. TheA limit switch 89 is normally biased to its closed position so that it will again close as soon as it is released by the dog 93. The opening of the limit vswitch The work piece |2 on the 89 also opens the sealing circuit for the actuating winding 09 of contact 89, however, thus permitting the contactor to move to its open position. Upon such opening of the contacts 99 of contactor 83, the solenoid 50 is deenergized and remains in such condition until the contactor 89 is again closed.

From the foregoing, it will be seen that at this point in the cycle of operation both of the solenoids 50 and 5| are deenergized so that both armatures move outwardly thereby moving the pivotal connection di to the rapid return position shown in dot-dash line in Figs. 2 and 8. This movement of the valve stem 89 actuates the valve member 2| to the position shown in Fig. 8 so that pressure uid is supplied to the machine tool actuating mechanism in such a manner as to effect a rapid return movement of the work table as was described above.

As soon as the table begins its rapid return movement, the dog 93 moves out of engagement 'with the normally closed limit switch 89 thus permitting the latter to close again. Such closure of the limit switch 89 does not, however, result in a re-closure of contacter 89 and reenergization of solenoid 50 since the limit switch 09 is located in the sealing circuit for the contactor rather than in the main energizing circuit. Upon continued rapid return movement of the table the dog 92 rides freely over the limit switch 8| so that it does not actuate the same. When the table ii iinally reaches its initial or starting position, however, a dog 9d engages the limit switch 8| and moves the same to its closed position. This again completes the energizing circuit for solenoid 9| so that the valve member 2| is moved to its neutral position shown in Fig. 5 as described above. As a result, the flow of pressure uid to the machine element actuating mechanism is cut od and the movement of the .table arrested.

The cycle of operation for the machine may again be initiated at will by closure of the starting push button 82. In the event of an emergency or for any other reason, the operation of the machine may be stopped at will by opening the stop push button 12. Such opening of this push button deenergizes the contactor windings 69 and 89 thus disconnecting the entire apparatus from the supply lines 59, 51 and 59.

In addition, the control mechanism may be moved to its neutral position at will at any time during the operation of the machine .without stopping the main drive motors 59 and 55. This is effected simply by the opening of stop push button 92 which opens the switch 03 thus deenergizing the solenoid 59. is deenergized and the solenoid 5| left energized as is the case upon the opening of push button 82, the control mechanism is moved to its neutral position thus stopping the movement of the table With the parts arranged for operation in the manner above described, it will be observed that there is no possibility of the valve mechanism becoming set for rapid approach motion on account of failure of power or for any othery cause. Also, failure of any one of the individual power actuated devices will ordinarily result in conditioning of the control mechanism for rapidreturn. Provision is therefore made for operation of the machine tool with optimum safety. Moreover, with the particulardifferential mechanism employed, it is unnecessary to move the controlling valve member from neutral to rapid ap- When the solenoid 50A proach position or from rapid approach to feed position without going through rapid return position and to move the member from feed to rapid return position without going through the rapid approach position.

Fig. 9 illustrates a modified form of control mechanism in which the valve shifting devices are energized by pressure fluid. In this embodiment, the flow of pressure fluid to the table actuating mechanism is governed by a valve which is identical with that shown in Figs. 5 to 8 and described above.

In general, the control mechanism in Fig. 9 includes two pressure iluid motors and |0| comprising cylinders |01 and |08 with pistons |09 and l0 therein having their rods |02 and |03 pivotally connected to the outer ends of a floating lever or equalizing link |04, which is in turn pivotally connected intermediate its ends to the valve operating stem 35. Tension springs |05 and |06 serve to normally bias the rods |02 and |09 respectively to theirextremity of movement in a right-hand direction as viewed in Fig. 9.

The cylinders |01 and |08 are provided with opposite ends. When pressure fluid is supplied to the cylinders |01 and |08 through ports ||2 and H4, respectively, the pistons |09 and ||0 will be moved to the left against the bias of the springs |05 and |08, respectively. The flow of pressure fluid from a pump I5 to the cylinders |01 and |08 is governed by a pair of distribution valves ||6 and ||1.

When the distributing valves ||6 and ||1 are in the position shown in Fig. 9, the cylinder |08 is energized or supplied with pressure fluid while the piston |09 is biased to the position illustrated by tension spring |05. Consequently, the valve operating stem 35 is maintained in the neutral position shown in Figs. 9 and 5 so that the supply of pressure fluid to the main machine tool actuating mechanism is cut ol as has been previously described and the table remains stationary.

Pressure fluid is supplied from the pump ||5 to the cylinder |08 to maintain the control mechanism in its neutral position through conduits ||8 and ||9, passage in valve ||1 andconduit |2|. On the other hand, pressure uid is suppli-ed from the pump ||5 through conduits ||8 and |22, passage |23 in valve ||6 and conduit |26 to port in the cylinder |01 so that the resulting movement of the piston |09 aids the tension spring |05 in moving the rods |02 to the right as viewed in Fig. 9. At the same time, the ports and ||3 of cylinders |01 and |08 are connected to an outlet conduit |25. Thus, upon reference to Fig. 9, it will be seen that the port ||2 is connected to the conduit |25 through a conduit |26, passage |21 in valve ||6, and conduit |28. Similarly, the port ||3 in the cylinder |08 is connected to the outlet conduit |25 through a conduit |29, passage |30 in valve ||1, and conduit |3|.

In order to initiate the cycle of operation of the machine tool, the valve ||6 is rotated 90 degrees in a counter-clockwise direction as viewed in Fig. 9 by a manual operating handle |32. This connects conduits v| 24 and |28 while passage |21 connects conduits |22 and |26. Thus, pressure fluid is supplied not only to the cylinder |08 of control member |0| to energize the same but also to cylinder |01. The iluid flows from the pump ||5 through conduits |22, valve passage |21 and conduit |26 to port ||2 of cylinder |01. As a result, both of the pistons |09 and ||0 are moved `tool are inoperative engagement. This arrangement includes a pivotally mounted dog |33 which ,is detachablysecured to the side of the table at any desiredfpoint. A stop pin |34 prevents movement of the dogv |33 in a clockwise direction beyond the ver-tical position illustrated so that` when the dog contacts a pivotally mounted operating fork |35 of the valve I1, it rotates the same approximately 90. degrees in a clockwise direction.

VSuch rotation of the valve ||1 serves to cut 01T the ow of pressure fluid to the cylinder |08 without cutting off the flow of pressure uid to the control member |00. Thus, the port ||4 of cyl- .inder |08 is connected to the outlet conduit |25 through conduit |2|, valve passage |30 and conduit 3| so that the pressure; on the right hand face of the piston is released. Also, pressure nuid is supplied to the port H3 of cy1inder los to aid in the retractive movement of the rod `|03 through conduits |29, valve passage |20, and y conduits I9 and ||8. At the same time, pressure g uid is supplied from the pump H to the port ||,2 of cylinder |01 through conduits IIB and |22, valve passage |23 and conduit |26. result, the valve operating stem 35 is moved to the position shown in Fig.'7 so that the fluid is supplied in reduced volume to the machine ,tool actuating mechanism and the movement of the table continues ata relatively slower feed rate.

An arrangement has been provided which is responsive to the movement of the table to a position in which the metal removing operation is completed for reversing the direction of movement of the table and causing it to be retracted at a rapid return rate. Thismovement is initiated by a pivotally mounted dog |36 which is detachably secured to the side of the table Il. Clockwise movement of the dog |36 is limited by a. stoppin |31 so that when the dog |36 engages a vforked operating member |38 on the valve ||6, the valve is rotated substantially 90 degrees in a clockwise direction to the position shown in Fig. 9. l In'such case, the ow o 'f pressure fluid is cut off to not onlythe port ||2 of cylinder |01 but also the port H4 of cylinder |08. Thus, the port ||2 is connected to the outlet conduit |25 through conduit |26, valve passage |21, and conduit |28, while port ||4l is connected to the outlet conduit |25 through conduit |2I, ,valve passage |30, and conduit |3| During the return movement of the table the dog |36 rides freely over the fork |38 without moving the valve IIB since `no stop pin is provided on the.

right-hand side of the dog |36. Similarly, the dog |33 also rides freely over the fork |35 without affecting the valve |1 since there is also no stop provided on the right-hand side of this dog.

'I'he rapid return movement of the table continues until a pivotally mounted dog |39 on the side of the table engages the valve operating fork |35. A stop pin |40 is provided on the righthand side of this dog. Such engagement of the dogv |39 with fork 35 rotates the valve ||1 in a counter-clockwise direction for substantially 90 degrees so that'it again assumes the position As a.

shown in Fig. 9. Thus, both the valves ||6 and ||1 are returned to their initial positions so that the control mechanism moves the valve stem 35 to its neutral position shown in Fig. 5 as described kinvention have been illustrated and described with some particularity for purposes of illustration, it should be understood'that no intention is to be inferred from this that the invention is to be limited to the particular constructionsshown and described, but on the other hand, the appended claims are intended to cover all modications within the spirit and scope of the invention.

I claim as my invention:

1. In a machine tool having a movable element, the combination of a single 'control member movable between two terminal positions through two intermediate positions, mechanism controlled by said member for causing rapid approach and rapid return motions of a machine tool element when said member is disposed in' the respective terminal positions, for causing movement of said element at a feed rate when thel member is in one of said intermediate positions, and for holding said element against movement when said member is in. the other'of said intermediate'positions, two independently movable devices, means individually biasing said devices in one direction, individual power actuators each adaptedwhen energized to move one of said devices against the action of its biasing means, and an equalizing bar connected at spaced points to the respective devices and intermediate said points to said member for moving said member to said rapid approach position when both of said actuators are energized, to rapid return position when neither of said actuators is energized, and in said intermediate `positions respectively when said actuators are individually energized.

2. In a machine tool having a movable element, the combination of a control member movable between two terminal positions through two intermediate positions, mechanisms controlled by said member for causing rapid approach and rapid return motions of said element when said member is disposed in the respective terminal positions, for causing movement of said element at a feed rate when the member is in` one of said intermediate positions, and for holding said element against movement when said member is in the other of said intermediate positions, two independently movable devices each biased for movement into one position, individual power actuators each adapted when energized to move one of said devices into a second position against the action of its biasing means, and differentially acting means for combining the motions of said devices and moving ysaid member to position the same in said rapid approach position when both of said actuators are energized, in rapid retum position when neither of vsaid actuators is energized, and in said intermediate positions respectivelyv when said actuators are individually energized.

3. In a machine tool having a movable element, the combination'of a single control member movable between two terminal positions through an intermediate position, mechanism controlled by said member for causing rapid approach and rapidreturn motions of said element when said member is disposed in thev respective terminal positions and for causing movement of said element at a1 feed rate when the member is in said intermediate position, two independently movable devices each biased for movement into oney position, two solenoids each adapted when energized to move one of saiddevices into a second position against the action of its biasing means, and differentially acting means for combining the motions of said devices and moving said member to position the same in said rapid approach position when both of said solenoids are energized, in rapid return position when neither of the solenoids is energized, and in said intermediate position when only one of the solenoids is energized.

4. In a machine tool having a movable element, the combination of a control member movable into at least three different positions, mechanism controlled by said member Afor causing movement of said element at rapid approach, rapid return and feed rates when said member is disposed in the respective positions, two independently movable devices each biased for movement in one direction, individual power actuators each adapted when energized to move one of said devices against the action of its biasing means, and means connecting said devices and said member and differentially combining the motions of said devices and moving said member to position the same in said rapid approach positionv when both of said actuators are energized, in rapid return position when neither of said actuators is energized, and in feed position when only one of said actuators is energized.

5. In a machine tool having a movable element, the combination of a control member movable into at least three different positions, mechanism controlled by said member for causing movement of said element at rapid approach, rapid return and feed rates when said member is disposed in the respective positions, two independently movable devices each biased for movement in one direction, individual power actuators4 each adapted when energized to move one' of said devices against the action of its biasing means, and an equalizinglever connected at opposite ends to the respective devices and intermediate 6. In a machine tool having a movable element, the combination of a single control member movable into three different positions, mechanism controlled by said member for causing movement of said element at rapid approach, rapid return and feed rates when said member is disposed in the respective positions, two independently movable devices each biased for movement in one direction, individual power actuators each adapted when energized to move one of said devices against the action of its biasing means, and means connecting said devices and acting differentially to combine the motions of said devices and moving said member to the respective positions according to whether one, both or neither of said actuators are energized, said member being moved to said rapid approach pol,

'7. In a machine tool having a movable element, the combination of a single control member movable into three different positions, mechanism controlled by said member for causing movement of said element at rapid approach, rapid return and feed rates when said member is disposed in the respective positions, two independently movable devices each biased for movement in one direction, individual power actuators each adapted when energized to move one of said devices against the action of its biasing means, and means connecting said devices and acting differentially to combine the motions of said devices and moving said member to the respective positions according to whether one, both or neither of said actuators are energized, said member being moved to said rapid return position when neither of said actuators is energized.

8. In a machine tool having a movable elenient, the combination of power driven means for actuating said element, mechanism controlling said driving means to effect movement of said element in diierent directions and at different rates including two independently movable devices each biased into a predetermined position and selectively operable in different combinations to cause movement of the element at rapid approach, rapid return and feed rates, and individual electromagnetic actuators each adapted when energized to move one of said devicesr `work support, a metal removing tool, power actuated mechanismfor effecting relative translatory movement of said work support and tool toward and away from each other, control means for said power actuated mechanism including a plurality of energizable electric solenoids, and means responsive to an interruption inthe voltage applied to said solenoids for causing said control means to `eiect relative movement of said work support and said tool away from each other.

10. In a machine tool, the combination of a work support, a tool support carrying a metalremoving tool, power actuated mechanism operable to produce forward and rapid return movements of one of said supports, control means selectively-operable to govern the operation of said mechanism to determine the direction and rate of movement of the .actuated support, and electrical devices energizable selectivelyto actuate said control means and operable when deenergized by interruption of the supply of energy to said control Ymeans to actuate the control means and cause movement f the actuated support in a direction to effect relative retractioiA between the tool and work supports whereby to utilize the momentum of the actuated support and said mechanism in coasting to a stop to carry said tool and the work piece on said work support out of engagement with each other.

MARION L. S'I'RAWN.

sition when both of said actuators are energized. 

